Multi-mode infinitely variable transmission

ABSTRACT

An infinitely variable transmission (IVT) includes a double planetary gearset with first, second, and third transmission components. The IVT includes a single planetary gearset with fourth, fifth, and sixth transmission components. In one mode, a first set of clutches is engaged, allowing transmission of engine power to the first transmission component, and allowing transmission of IVP power between a second IVP machine and the second transmission component. The third transmission component combines the engine power and the IVP power into first combined power that is transmitted from the third transmission component to the fourth transmission component. The fifth transmission component transmits return power to an engine shaft, and the sixth transmission component combines the first combined power and the return power into second combined power that is output to an output shaft for rotating the output shaft at a range of rotational speeds.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of U.S. application Ser. No.14/536,097, filed Nov. 7, 2014, which is a continuation-in-part of U.S.application Ser. No. 14/145,599, filed on Dec. 31, 2013, and issued asU.S. Pat. No. 9,206,885 on Dec. 8, 2015, the entire disclosure of eachbeing incorporated by reference herein.

STATEMENT OF FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

Not applicable.

FIELD OF THE DISCLOSURE

This disclosure relates to infinitely variable transmissions and, moreparticularly, to an infinitely variable transmission with a plurality ofdifferent powered modes.

BACKGROUND OF THE DISCLOSURE

It may be useful, in a variety of settings, to utilize both atraditional engine (e.g., an internal combustion engine) and aninfinitely variable power source (e.g., an electric or hydrostaticmotor, a variable chain drive, and so on) to provide useful power. Forexample, a portion of engine power may be diverted to drive a firstinfinitely variable machine (e.g., a first electric machine acting as agenerator), which may in turn drive a second infinitely variable machine(e.g., a second electric machine acting as a motor using electricalpower from the first electrical machine). In certain configurations,power from both types of sources (i.e., an engine and an infinitelyvariable power source) may be combined for final power delivery (e.g.,to a vehicle axle) via an infinitely variable transmission (“IVT”) orcontinuously variable transmission (“CVT”). This may be referred to as“split-mode” or “split-path mode” operation because power transmissionmay be split between the mechanical path from the engine and theinfinitely variable path. Split-mode operation may be attained invarious known ways. For example, a planetary gear set may be utilized tosum rotational power from an engine and from an electric machine, withthe summed power transmitted downstream within an associated powertrain.This may allow for delivery of power (e.g., to vehicle wheels) with aninfinitely variable effective gear ratio. Various issues may arise,however, including limitations relating to the maximum practical speedof variable power sources.

The operation of other types of transmissions, as well as IVT or CVTtransmissions, may introduce various other issues. For example, incertain configurations, transmission shifts (e.g., transitions betweendifferent gear ratios) may result in jolts to a vehicle, lags or othertransient effects on available power (e.g., at the wheels of a vehicleor at an attached tool or implement), or other detrimental effects onsystem performance and user experience.

SUMMARY OF THE DISCLOSURE

In one aspect, the disclosure provides a work vehicle that includes anengine with an engine shaft, a first infinitely variable power (IVP)machine, a second infinitely variable power (IVP) machine, an outputshaft, and an infinitely variable transmission (IVT) having a pluralityof transmission modes. The IVT is configured to transmit power among theengine, the first IVP machine, the second IVP machine, and the outputshaft along different paths in different ones of the plurality oftransmission modes. The IVT includes a plurality of clutches, eachconfigured to engage and alternately disengage. Moreover, the IVTincludes a double planetary gearset including a first transmissioncomponent, a second transmission component, and a third transmissioncomponent. Furthermore, the IVT includes a single planetary gearsetincluding a fourth transmission component, a fifth transmissioncomponent, and a sixth transmission component. In a first transmissionmode of the IVT, a first subset of the plurality of clutches is engaged,allowing transmission of engine power from the engine to the firsttransmission component, and allowing transmission of IVP power betweenthe second IVP machine and the second transmission component. In thefirst transmission mode, the third transmission component combines theengine power and the IVP power into first combined power that istransmitted from the third transmission component to the fourthtransmission component. In the first transmission mode, the fifthtransmission component transmits return power to the engine shaft, andthe sixth transmission component combines the first combined power andthe return power into second combined power that is output to the outputshaft for rotating the output shaft at a range of rotational speeds.

In another aspect, a work vehicle is disclosed that includes an enginewith an engine shaft and an infinitely variable power (IVP) sourcehaving a first electric machine and a second electric machine. The workvehicle further includes an output shaft and an infinitely variabletransmission (IVT) having a plurality of transmission modes. The IVT isconfigured to transmit power among the engine, the first electricmachine, the second electric machine, and the output shaft alongdifferent paths in different ones of the plurality of transmissionmodes. The IVT includes a plurality of clutches, each configured toengage and alternately disengage. The IVT further includes a firstplanetary gearset including a first transmission component, a secondtransmission component and a third transmission component. Additionally,the IVT includes a second planetary gearset including a fourthtransmission component, a fifth transmission component, and a sixthtransmission component. In a first transmission mode of the IVT, a firstsubset of the plurality of clutches is engaged, allowing transmission ofengine power from the engine to the first transmission component, andallowing transmission of IVP power between the second electric machineand the second transmission component. In the first transmission mode,the third transmission component combines the engine power and the IVPpower into first combined power that is transmitted from the thirdtransmission component to the fourth transmission component.Additionally, in the first transmission mode, the fifth transmissioncomponent transmits return power to the engine shaft. Also, in the firsttransmission mode, the sixth transmission component combines the firstcombined power and the return power into second combined power. Thesecond combined power of the first transmission mode provides the outputshaft with a range of rotational speeds. The first electric machine hasa generator mode and a motor mode. The first electric machine, when inthe generator mode, is configured to generate electrical energy frommechanical energy input to the first electric machine. Also, the secondelectric machine has a generator mode and a motor mode. The secondelectric machine, when in the generator mode, is configured to generateelectrical energy from mechanical energy input to the second electricmachine. In the first transmission mode of the IVT, the first electricmachine and the second electric machine are configured to simultaneouslybe in generator mode for cogeneration of electrical power.

The details of one or more embodiments are set forth in the accompanyingdrawings and the description below. Other features and advantages willbecome apparent from the description, the drawings, and the claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a side view of an example work vehicle that may include aninfinitely variable transmission;

FIG. 2 is a schematic view of a powertrain of the vehicle of FIG. 1;

FIG. 3 is a schematic view of an infinitely variable transmission thatmay be included in the powertrain of FIG. 2;

FIG. 4 is a graphical representation of infinitely variable power sourcespeeds and vehicle wheel speeds for various modes of operation of theinfinitely variable transmission of FIG. 3;

FIG. 5 is a schematic view of another infinitely variable transmissionthat may be included in the powertrain of FIG. 2;

FIG. 6 is a graphical representation of infinitely variable power sourcespeeds and vehicle wheel speeds for various modes of operation of theinfinitely variable transmission of FIG. 5;

FIG. 7 is a schematic view of another infinitely variable transmissionthat may be included in the powertrain of FIG. 2;

FIG. 8 is a graphical representation of variable power source speeds andvehicle wheel speeds for various modes of operation of the infinitelyvariable transmission of FIG. 7;

FIG. 9 is a schematic view of a powertrain similar to that of FIG. 3,with a power storage and delivery system;

FIG. 10 is a schematic view of a powertrain similar to that of FIG. 7,with another power storage and delivery system;

FIG. 11 is a diagrammatic view of a transient power event managementprocess, which may be used with the powertrains of FIGS. 9 and 10;

FIG. 12 is a schematic view of a powertrain related to that of FIG. 3,wherein the powertrain is shown in a first configuration;

FIG. 13 is a graph representing the wheel speed of a vehicle versus arotational speed of an electric machine of the powertrain of FIG. 12 fora given engine speed according to example embodiments of the presentdisclosure;

FIG. 14 is a schematic view of the powertrain of FIG. 12 shown in asecond configuration;

FIG. 15 is a schematic view of a powertrain related to that of FIG. 12,wherein the powertrain is shown in a first configuration; and

FIG. 16 is a schematic view of the powertrain of FIG. 15 shown in asecond configuration.

Like reference symbols in the various drawings indicate like elements.

DETAILED DESCRIPTION

The following describes one or more example embodiments of the disclosedpowertrain arrangement for energy storage and delivery, as shown in theaccompanying figures of the drawings described briefly above. Variousmodifications to the example embodiments may be contemplated by one ofskill in the art.

In various known configurations, one or more planetary gear sets may beutilized to combine the power output of an IVP and an engine (e.g., aninternal combustion engine). For example, in a planetary gear set afirst component of the gear set (e.g., a ring gear) may receive powerfrom the engine, a second component of the gear set (e.g., a sun gear)may receive power from the IVP, and a third component of the gear set(e.g., a planet gear carrier) may sum the power from the engine and theIVP at the output of the gear set. (For convenience of notation,“component” may be used herein, particularly in the context of aplanetary gear set, to indicate an element for transmission of power,such as a sun gear, a ring gear, or a planet gear carrier.) It will beunderstood that such a configuration may allow for essentially infiniteand continuous gear ratios for the planetary gear set. For example, fora fixed engine speed, a particular gear ratio may be set by varying thespeed of the IVP with respect to the engine speed.

In certain instances, it may be useful to facilitate a powered-zero modefor a vehicle (or other machinery), in which the output speed of thevehicle wheels (or other machinery output) reaches zero speed withoutstopping the engine or releasing torque at the wheels. In this way, forexample, vehicle power may be utilized to hold a vehicle stationary.Such a state may be obtained, for example, with a planetary gear setconfigured as described above. For example, if an engine is spinning asun gear at a first positive speed and an IVP (e.g., an electric motorpowered by a generator) is directed to spin a ring gear at an equivalentnegative speed, an associated planet gear carrier (which may, forexample, be connected to a differential drive shaft) may not spin atall. Further, if the IVP provides an output rotation at a slightlydifferent (and opposite) speed from the engine, the vehicle may enter a“creeper” mode, in which the vehicle moves very slowly but with highwheel torque. The powered-zero and creeper modes are particularly usefulfor heavy-duty work vehicles, such as the tractor shown in FIG. 1, usedin the agricultural, construction and forestry industries. Withincreasing wheel speed, the vehicle may then, eventually, enter a normaldrive mode. In traditional configurations, each of these modes may besplit-path modes, in which power transmission is split between a purelymechanical path from the engine and the mixed path through the IVP.

One issue relating to infinitely variable powertrains may concern therelative efficiency of power transmission in various modes. It will beunderstood, for example, that mechanical transmission of power from anengine to a gear set (i.e., mechanical path transmission) may be ahighly efficient mode of power transmission, whereas transmission ofpower through an IVP may be less efficient (e.g., because the mechanicalpower must be converted to electrical or hydraulic power by a firstmachine, transmitted to a second machine, and then converted back tomechanical power). Accordingly, there may exist significant motivationto utilize the mechanical path more heavily than the IVP path (e.g., byincreasing the speed of the engine). However, this heavier utilizationof the mechanical path may also drive up the required IVP speed forpowered-zero and creeper modes, because these modes may require near oractual speed matching between the IVP and engine speeds. This may leadto increased wear on related gears and other parts (e.g., a planetarygear component receiving power from the IVP and associated bearings),even to the point of part failure. Further, to attain appropriatespeeds, the size and power of a relevant IVP may need to besignificantly increased from a preferred size and power. Among otheradvantages, the multi-mode infinitely variable transmission (“MIVT”)disclosed herein may address these issues. For example, throughselective use of clutches and/or brakes, an MIVT may allow heavierutilization of a mechanical path, while avoiding the need for excessiveIVP speeds in powered-zero and creeper modes.

As will become apparent from the discussion herein, an MIVT may be usedadvantageously in a variety of settings and with a variety of machinery.For example, referring now to FIG. 1, an MIVT may be included in thepowertrain 22 of a vehicle 20. In FIG. 1, the vehicle 20 is depicted asa tractor. It will be understood, however, that other configurations maybe possible, including configuration of vehicle 20 as a different kindof tractor, as a log skidder, as a grader, or as one of various otherwork vehicle types. It will further be understood that the disclosed IVTmay also be used in non-work vehicles and non-vehicle applications(e.g., fixed-location powertrains).

As also noted above, one advantage of the disclosed MIVT is that it mayallow operation of a vehicle in a variety of powered modes (e.g.,powered-zero mode, creeper mode, and split-path drive mode), which mayutilize various combinations of engine and IVP power. For example,through the use of various clutches and/or brakes associated with one ormore planetary gear sets, an MIVT may permit engine power to bedisconnected from a IVT output, even while the engine continues tooperate. For example, if an IVP drives a first component of a planetarygear set and an engine drives a second component of the planetary gearset, in certain embodiments and modes a clutch may disconnect theoperating engine from the second component and a brake may stop rotationof a third component of the gear set, thereby allowing delivery of powersolely from the IVP through the gear reduction of the planetary gearset. In this way, for example, only electrical power (or hydraulicpower, and so on) may be utilized to drive (or hold) the vehicle 20 incertain modes, while combined electrical and engine power may beutilized to drive (or hold) the vehicle 20 in other modes. As such,among other benefits, an MIVT may avoid certain previous limitations onthe fraction of power that may diverted from an engine through anelectric path (or hydraulic path, and so on).

Referring now to FIG. 2, various components of an example powertrain 22are depicted. For example, an engine 24 may provide mechanical power(e.g., via a rotating shaft) to an MIVT 26. The engine 24 may alsoprovide mechanical power to an IVP 28, which may include one or more IVPmachines (e.g., an electric motor and generator, or hydrostatic machinehaving a hydrostatic motor and associated pump). The MIVT 26 a mayadditionally receive mechanical power from the IVP 28.

The MIVT 26 a may include various clutches 30 and brakes 32, which maybe controlled by various actuators 34. The actuators 34, in turn, may becontrolled by a transmission control unit (“TCU”) 36 (or anothercontroller), which may receive various inputs from various sensors ordevices (not shown) via a CAN bus (not shown) of the vehicle 20. TheMIVT 26 a may include one or more output shafts 38 a for transmission ofmechanical power from the MIVT 26 a to various other components (e.g., adifferential drive shaft). In certain embodiments, additional gear sets(e.g., a set of range gears) may be interposed between the MIVT 26 andother parts of the vehicle 20 (e.g., a differential drive shaft). Incertain embodiments, the IVP 28 may also provide power directly to otherparts of the vehicle 20 (e.g., via direct IVP drive shaft 38 b).

Referring now to FIG. 3, various internal components of an example MIVT26 a are presented. It should be noted that the schematicrepresentations of the transmission shown in FIG. 3 (and also thetransmissions shown in FIGS. 5 and 7) illustrate example implementationsin simplified form for clarity, and thus may not depict all of thecomponents associated with the represented transmission. The engine 24may include an internal combustion engine 24 a, which may providemechanical power directly to a shaft S1. (As used herein, “direct” powertransmission may include transmission of power by direct physicalconnection, integral formation, or via a simple intervening element suchas an idler gear or planet gear. In contrast, for example, powertransmission between a ring gear of a planetary gear set and a sun gearof the planetary gear set via a planet gear carrier (and associatedplanet gears) of the planetary gear set may not be considered “direct.”)An example IVP 28 a may include an electric generator 40 and an electricmotor 42. The electric generator 40 may receive mechanical power via agear 46 and a gear 44, attached to the shaft S1, and may generateelectrical power for transmission to an electric motor 42. The electricmotor 42 may convert the received electrical power to mechanical powerand thereby rotate a shaft S2.

Although specific terms such as “generator” and “motor” may be usedherein to describe various example configurations, it will be understoodthat these (and similar) terms may be used to refer generally to anelectrical machine that may be capable of operating either as agenerator or as a motor. For example, the electric generator 40 maysometimes operate as an electric motor, and the electric motor 42 maysometimes operate as a generator. Likewise, it will be understood thatthe actual operating modes of other infinitely variable power sourcesmay similarly vary from those explicitly described herein.

In certain embodiments, the MIVT 26 a may include a planetary gear set48 and a double planetary gear set 50. In certain embodiments, theplanetary gear set 48 and the double planetary gear set 50 may beconfigured to sum mechanical power from the engine 24 a and the IVP 28a. Through the use of one or more associated clutches and/or brakes, theMIVT 26 a may provide an output, in certain modes, that utilizes onlypower from IVP 28 a.

The planetary gear set 48 may include, for example, a planet gearcarrier 52 holding planet gears 54, which may be meshed with a sun gear56 and ring gear 58. Drive clutch 60 may be configured to engage planetgear carrier 52 and sun gear 56 (e.g., based upon signals from TCU 36)in order to control power transmission between these gears. For example,in a fully engaged state, drive clutch 60 may lock planet gear carrier52 to sun gear 56. As depicted in FIG. 3, engine 24 a may directly driveplanet gear carrier 52 via shaft S1. Accordingly, engagement of clutch60 may effectively lock sun gear 56 to shaft S1 and the output of engine24 a. Reverse brake 62 may be anchored to a fixed housing of MIVT 26 a(or another feature) and may be configured to engage to stop therotation of ring gear 58.

In certain embodiments, an output component of the planetary gear set 48may directly transmit power to an input component of the doubleplanetary gear set 50. For example, the sun gear 56 may be integrallyconnected with the ring gear 64, thereby directly connecting an outputof planetary gear set 48 (i.e., the sun gear 56) to an input to doubleplanetary gear set 50 (i.e., the ring gear 64).

The double planetary gear set 50 may also receive power input from theIVP 28 a. For example, the electric motor 42 may drive the rotation ofthe shaft S2, along with an attached gear 66. The gear 66 may be meshedwith a gear 68, mounted to the shaft S1, and the gear 68 may directlytransmit power to (e.g., may be integrally formed with) a sun gear 70 ofthe double planetary gear set 50. The sun gear 70 may mesh with planetgears 72 (one shown), which may be directly connected with planet gears74 (one shown), both sets of the planet gears 72 and 74 being carried bya planet gear carrier 76. Each of the planet gears 74 may mesh with oneof various planet gears 88, which in turn may mesh with a ring gear 78.The planet gear carrier 76 may connect to the ring gear 78 (e.g., viaplanet gears 74 and 88), and a creeper brake 80 may be anchored to afixed housing of the MIVT 26 a (or another feature) and configured toengage the ring 78 to stop the rotation of that component.

Planet gear carrier 76 may provide a mechanical power output from thedouble planetary gear set 50 for transmission of mechanical power tovarious parts of the vehicle 20. For example, the planet gear carrier 76may be integrally connected with an output gear 82, which may be meshedwith a gear along an idler shaft S3. In certain embodiments, anadditional gear box 84 (e.g., a range gear box) may be interposedbetween the MIVT 26 a and other parts of the vehicle 20 (e.g., adifferential drive shaft (“DDS”)) or may be included as part of the MIVT26 a. In this way, for example, various gear shifts may be implementedover the baseline infinitely variable gear ratio provided by the MIVT 26a.

In certain modes of operation, the MIVT 26 a (as configured in FIG. 3)may provide for powered-zero and creeper modes in which only power fromthe IVP 28 a is provided to the wheels of the vehicle 20. For example,the drive clutch 60 may be disengaged and the brake 80 may be engagedwith the ring gear 78 (or, in certain configurations, with the ring gear64 (not shown)). This may, accordingly, disconnect the engine 24 a fromthe double planetary gear set 50, while providing a fixed gear (e.g.,the ring gear 78) around which the components of the double planetarygear set 50 may rotate. Mechanical power from the IVP 28 a may beprovided to the sun gear 70, which may drive the planet carrier 76around the ring gear 78. This may, in turn, cause rotation of the outputgear 82, driven by the IVP 28 a but not by the engine 24 a, which mayallow for the driving of the wheels of the vehicle 20 (e.g., via thegear box 84) using only power from the IVP 28 a.

In order to shift the vehicle out of this IVP-only mode, a reverseprocess to that described above may be executed. For example, the driveclutch 60 may be engaged, thereby connecting the engine 24 a to the sungear 56 and the ring gear 64. At the same time (or nearly the sametime), the creeper brake 80 may be disengaged, thereby allowing thedouble planetary gear set 50 to provide an output at the gear 82 thatrepresents a sum of the power from the IVP 28 a and the engine 24 a. Itwill be understood that this selective use of two of a set of frictionelements (e.g., clutches and brakes) may generally facilitate transitionbetween various operating modes for the vehicle 20.

In certain embodiments, it may be beneficial to effect a transitionbetween modes (e.g., between an all-IVP creeper mode and a combineddrive mode) in particular ways. For example, with the drive clutch 60engaged, it may be possible to spin the sun gear 70 (via the IVP 28 a)at a speed such that the ring gear 78 essentially stops, even withoutuse of the brake 80. In order to provide for more seamless shiftingbetween modes, it may be beneficial to shift between drive and creepermode at such a point. In this way, for example, the brake 80 may beengaged and the clutch 60 may be disengaged with minimal disruption tovehicle operation. A similar seamless shift point may also be obtainedfor shifts from creeper to drive modes, and may represent a target pointfor those shift operations (and others). It will be understood, however,that in certain embodiments ramped (or other) modulation of the clutch60 (or other components) may be utilized.

In certain applications, it may be desirable to operate the vehicle 20in reverse, whether in creeper mode, drive mode, or otherwise. In theMIVT 26 a as depicted in FIG. 3, for example, it may be possible toengage the reverse brake 62 for this purpose.

Referring now to FIG. 4, a graph is presented of the relationshipbetween vehicle wheel speed (in kilometers per hour) and the speed ofthe electric motor 42 (in revolutions per minute) for the configurationof the MIVT 26 a in FIG. 3. Various curves are presented for operationof the vehicle 20 with various range gears (not shown) engaged withinthe gear box 84. It will be understood that the quantities representedin FIG. 4 should be viewed as examples only.

A line 90, for example, may represent operation of the vehicle in acreeper mode (e.g., under electrical power only). It can be seen that atzero motor speed there may be zero vehicle speed, with non-zero motorspeed directly proportional to vehicle speed. In creeper mode (e.g.,with the brake 80 engaged, the drive clutch 60 disengaged, and anA-range gear (not shown) in the gear box 84 engaged), the vehicle 20 mayaccelerate to a transition point. For example, as described above, thevehicle 20 may accelerate to a point at which, based on the engine speedand relevant gear ratios, the ring 78 may be relatively stationary evenwithout engagement of the brake 80. At this point (or another), thebrake 80 may be disengaged and the clutch 60 engaged, thereby shiftingthe vehicle 20 into split-mode drive relatively seamlessly. The motor 42may then begin to decelerate along a line 92, with vehicle speed (nowdriven in split-path mode by both the motor 42 and the engine 24 a)increasing even as the speed of the motor 42 changes direction (i.e.,passes from positive rotation to negative rotation).

Continuing, the vehicle 20 may be shifted from the A-range gear in thegear box 84 to a higher B-range gear (not shown). To continueacceleration of the vehicle 20, it may now be appropriate to switch thedirection of the rotation of the motor 42, thereby jumping from negativerotation and the line 92 to positive rotation and a line 94. The motor42 may then be decelerated again, followed by a further shift to ahigher C-range gear (not shown) in the gear box 84 and a correspondingjump, for the motor 42, from the line 94 to a line 96. By modulating therotation of the motor 42 in this way, shifts between various range gearsof the gear box 84 may be accomplished with the same reduction ratio atthe start of the shift (e.g., at the end of A-range driving) as at theend of the shift (e.g., at the beginning of B-range driving). (It willbe understood that a reduction ratio may be the product of the gearratios of the planetary gear sets 48 and 50 and the engaged gear (e.g.,the A-range gear) of the gear box 84.)

Various benefits may obtain from the configuration of FIG. 3 (and otherscontemplated by this disclosure). For example, in the configuration ofFIG. 3 (and other configurations) the gear box 84 may be locateddownstream of the planetary gear sets 48 and 50. This may allow the useof the full range of torques and speeds resulting at the output of theMIVT 26 a (i.e., as may result from the various combinations of thepower of the engine 24 a and the motor 42) with each range or gear ofthe gear box 84. For example, an electric-only mode (or any of a varietyof split-path modes) may be utilized with each range or gear of the gearbox 84. This may provide significant flexibility during vehicleoperation.

Additionally, in the configuration of FIG. 3 (and other configurations)split-mode drive may be implemented using a relatively simple planetarypath, which may decrease wear, improve life, and decrease costs for theMIVT 26 a, among other benefits. This may be particularly useful, forexample, for applications in which a majority of operating time isexpected to be spent in split-path mode (e.g., for various agriculturaloperations conducted with the vehicle 20). In split-path mode, forexample, power from the engine 24 a may be provided through the clutch60 to the ring gear 64, and power from the motor 42 being provided tothe sun gear 70. These components (i.e., the ring gear 64 and the sungear 70) may together cause rotation of the planet carrier 76 (via theplanet gears 72), which in turn may cause rotation of the gear 82 andthe corresponding transfer of power into the gear box 84. In contrast,in an electric-only mode, power from the motor 42 may be provided to thesun gear 70 and then, in turn, to the planet gears 72, the planet gears74 (which may be directly connected to or integrally formed with thegears 72), and the planet gears 88. With the ring gear 78 locked by thebrake 80, power may then flow from the planet gears 72, 74 and 88 to theplanet carrier 76, and so on. In this way, it will be understood, fewergear meshes may be utilized in the split-path power mode than in theelectric-only mode, which may represent a relative improvement in powertransfer efficiency and may also result in a relative decrease in partwear.

Referring now also to FIG. 5, another example MIVT 26 b is presented. Asdepicted in FIG. 5, the MIVT 26 b may include planetary gear set 98 anda double planetary gear set 100. An internal combustion engine 24 b maydirectly drive both a hydrostatic drive (e.g., a pump 102 and a motor104) and a shaft S4, and the hydrostatic drive (e.g., via the motor 104)may drive a shaft S5. A planetary gear set 98 may include a sun gear106, a planet gear carrier 108, and a ring gear 110. A drive clutch 112may be configured to engage with the shaft S4 in order to connect theoutput of the engine 24 b to the sun gear 106. A creeper clutch 114 maybe configured to engage both the planet gear carrier 108 and the ringgear 110, thereby potentially locking the planet gear carrier 108 andthe ring gear 110 together. A reverse brake 116 may be configured toengage the ring gear 110. In certain configurations, accordingly, thereverse brake 116 may be utilized to reverse the output of the planetarygear set 98 with respect to the output of the engine 24 b.

The planetary gear set 98 may include an output that is directlyconnected (e.g., directly geared to or integral with) an input to thedouble planetary gear set 100. For example, as depicted in FIG. 5, theplanet gear carrier 108 may be an output component for the planetarygear set 98 and may be directly geared (i.e., via gears 118 and 120) toa planet gear carrier 122 of the double planetary gear set 100. Further,in certain configurations, this input to the gear set 100 may rotatedirectly with another component of the gear set 100. For example, theplanet gear carrier 122 may be formed as an integral component with aring gear 124, such that both components rotate in unison.

The motor 104 may provide an additional input to the double planetarygear set 100. For example, via the shaft S5, the motor 104 may provideinput power to both of sun gears 126 and 128. The double planetary gearset 100 may also include, for example, a ring gear 130, and a planetgear carrier 134.

In this configuration, similar to the discussion above regarding theembodiment of FIG. 3, various clutches and brakes associated with theMIVT 26 b may be utilized to switch between various operating modes forthe vehicle 20. For example, when the drive clutch 112 is disengagedpower may not be transmitted from the operating engine 24 b to theplanetary gear set 98 or the double planetary gear set 100. Further,with the creeper clutch 114 engaged and the reverse brake 116 engaged,the gear 118 may be locked. Accordingly, engagement of the creeperclutch 114 and the reverse brake 116 may prevent rotation of both thering gear 124 and the planet gear carrier 122 (although planet gears 132may still rotate around the carrier 122). In this way, even though theengine 24 b may be operating, the double planetary gear set 100 maytransmit to an output gear 140 only power from the motor 104 (e.g., ineither a forward or a reverse creeper-mode).

In certain embodiments, additional power-transfer components may beprovided to facilitate various types of vehicle operation andoperational modes. For example, a low clutch 136 and a high clutch 138may be included within the double planetary gear set 100, with the highclutch 138 configured to engage both the ring gear 130 and the outputgear 140, and with the low clutch 136 configured to engage both theplanet gear carrier 134 and the output gear 140. Accordingly, in creeperor other modes, the clutches 136 and 138 may be selectively activated inorder to adjust the effective total gear ratio of the two planetary gearsets 98 and 100.

In certain embodiments, a gear box 142 may be interposed between thedouble planetary gear set 100 and other parts of the vehicle 20 (e.g., aDDS), and may include various gears (e.g., range gears). Also in certainembodiments, the configuration represented in FIG. 5 may allowtransition between fixed gear ratios within the gear box 142 (and in thecontext of the infinitely variable gear ratio provided by thehydrostatic machines 102, 104) without necessarily changing thedirection of rotation for the motor 104. For example, the vehicle 20 maystart operation at zero speed, with the engine 24 b disconnected fromthe transmission (via the clutch 112) and with the clutch 114 and thebrake 116 engaged. The motor 104, accordingly, may provide the solepower to the output gear 140 (and the gear box 142). The motor 104 maybe started in the positive direction (for positive-direction creepermode operation) or negative direction (for negative-direction creepermode operation). Assuming, for example, an initial positive direction oftravel, rotation of the motor 104 (and thereby the shaft S5) mayaccelerate in the positive direction, causing the sun gears 126, 128 toalso accelerate. Initially, for example, the low clutch 136 may beengaged, whereby power may be transferred from the sun gear 128, via theplanet gear carrier 134 to the output gear 140. Within the gear box 142,a first low range gear may be engaged, thereby completing the powertransmission path from the motor 104 to other parts of the vehicle 20(e.g., a differential drive shaft).

At a particular speed of the motor 104, depending on the particularassociated gear ratios, the ring gear 110 may tend to be relativelystationary, even when the brake 116 is not engaged. As also noted above,this may provide a useful point at which to transition between operationmodes (e.g., creeper mode and split-path mode) or various gears (e.g.,range gears within the gear box 142). Accordingly, continuing theexample above, once the motor 104 has accelerated through creeper modeto such a speed-matched point (or at various other times), the reversebrake 116 may be disengaged and the drive clutch 112 may be engaged.This may provide a mechanical transmission path for power from engine 24b to the double planetary gear set 100. At the same time (or nearly thesame time), the low clutch 136 may also be disengaged and the highclutch 138 may be engaged. However, due to the configuration representedin FIG. 5, it may not be necessary at this point to reverse therotational direction of the motor 104 in order to continue forwardacceleration of the vehicle 20 (as it may be, for example, for theconfiguration represented in FIG. 3). In certain embodiments, afterengagement of the clutch 112 (i.e., entry into a split-path mode), therotational speed of the motor 104 may simply be decelerated from therotational speed at the time of the transition, with the vehicle 20accelerating accordingly.

Referring now to FIG. 6, for example, a graph is presented of therelationship between vehicle wheel speed (in kilometers per hour) andthe speed of the motor 104 (in revolutions per minute) for theconfiguration of the MIVT 26 b in FIG. 5. Various curves are presentedfor operation of the vehicle 20 with various gears (e.g., range gears)engaged within the gear box 142. It will be understood that thequantities represented in FIG. 6 should be viewed as examples only.

A line 150, for example, may represent operation of the vehicle 20 in acreeper mode (e.g., under hydrostatic power only). It can be seen thatat zero motor speed there may be zero vehicle speed, with non-zero motorspeed being directly proportional to vehicle speed. In creeper mode(e.g., with the reverse brake 116 and the creeper clutch 114 engaged,the drive clutch 112 disengaged, and an A-range gear (not shown) in thegear box 142 engaged), the vehicle may accelerate to a transition point.In certain embodiments, this may be a point at which, based on theengine speed and relevant gear ratios, the ring gear 110 may berelatively stationary even without engagement of the brake 116. At thistransition point (or another), the brake 116 may be disengaged and theclutch 112 engaged, thereby shifting the vehicle into split-mode drive.The motor 104 may then begin to decelerate along a line 152, withvehicle speed (now driven by both the motor 104 and the engine 24 b)increasing even as the speed of the motor 104 changes direction (i.e.,passes from positive rotation to negative rotation).

Continuing, the vehicle may be shifted from the former A-range gear inthe gear box 142 to a higher B-range gear (not shown). To continueacceleration of the vehicle 20, it may again be appropriate to switchthe direction acceleration of the rotation of the motor 104 (but not,immediately, the direction of rotation of the motor 104), and engage anappropriate range gear (with or without switching among the clutches 136and 138). The motor 104 may then accelerate along a line 154, with thevehicle 20 accelerating accordingly.

Referring now to FIG. 7, an additional example MIVT 26 c is presented.As depicted in FIG. 7, an internal combustion engine 24 c may providemechanical power to an electric generator 172, which may provideelectrical power to an electric motor 174 via a power cable 176. Themotor 174 may (e.g., via direct gearing) drive rotation of a sun gear182 of a double planetary gear set 178. The gear set 178 may also beconfigured to receive mechanical power from the engine 24 c via a shaftS7, with a drive clutch 196 configured to engage both the shaft S7 andanother sun gear 180. A planet gear carrier 184, including planet gears192 may be directly connected to (e.g., integral with) a ring gear 190,which may itself be configured to receive power from the sun gear 182via a planet gear carrier 186. A ring gear 188 may be meshed with theplanet gears 192. Further, the planet gear carrier 186 may form anoutput component of the gear set 178 and may, for example, be directlyconnected to (e.g., integrally formed with) an input component of a gearbox 202.

As in other embodiments discussed herein, a number of clutches andbrakes within the MIVT 26 c (e.g., as represented in FIG. 7) may allowfor useful transition between various operating modes, including acreeper mode powered only by the motor 174 and a split-path mode poweredby both the motor 174 and the engine 24 c. For example, the clutch 196may engage with the shaft S7 and the sun gear 180 in order to transmitpower from the engine 24 c to the double planetary gear set 178.Likewise, a clutch 198 may engage both the ring gear 188 and the planetgear carrier 184 in order to lock these components together. Finally, areverse brake 200 may engage the ring gear 188 in order to stop rotationof that gear.

In this light, it will be understood that the clutch 198, the brake 200and the clutch 196 may be selectively engaged (and disengaged) in orderto provide for various modes of operation. For example, with the clutch196 disengaged and both the clutch 198 and the reverse brake 200engaged, the vehicle 20 may be driven under the power only of the motor174. Likewise, other operational modes may be possible with variousother configurations (e.g., various combinations in which two of theclutch 198, the brake 200, and the clutch 196 are engaged).

Referring now also to FIG. 8, for example, a graph is presented of therelationship between vehicle wheel speed (in kilometers per hour) andthe speed of the motor 174 (in revolutions per minute) for theconfiguration of the MIVT 26 c in FIG. 7. Various curves are presentedfor operation of the vehicle 20 with various gears (e.g., range gears)engaged within the gear box 202. It will be understood that thequantities represented in FIG. 8 should be viewed as examples only.

A line 212, for example, may represent operation of the vehicle 20 in acreeper mode (e.g., under electrical power only). It can be seen that atzero motor speed there may be zero vehicle speed, with non-zero motorspeed relating proportionally to vehicle speed. In creeper mode (e.g.,with the reverse brake 200 and the clutch 198 engaged, the drive clutch196 disengaged, and an A-range gear (not shown) in the gear box 202engaged), the vehicle 20 may accelerate to a transition point. Forexample, the vehicle 20 may accelerate to a point at which, based on theengine speed and relevant gear ratios, the ring gear 188 may berelatively stationary even without engagement of the brake 200). At thispoint (or another), the clutch 198 may be disengaged and the clutch 196engaged, thereby shifting the vehicle into split-mode drive. At thistime (or near this time) the motor 174 may then reverse its direction ofrotation, thereby transitioning from the line 212 to a line 214. Thevehicle 20, accordingly, may continue to accelerate (now driven by boththe motor 174 and the engine 24 c), with vehicle speed increasing evenas the speed of the motor 174 changes direction (i.e., passes fromnegative rotation to positive rotation). Similar shifts may also beeffected, for example, into a B-range gear (not shown) from the A-rangegear (not shown) by transitioning the motor 174 from the line 214 to aline 216, and so on.

In certain embodiments, including with regard to various transmissionconfigurations discussed above, it may be useful to provide a powertrainarrangement with energy storage and delivery (“ESD”) capability forpowering vehicle systems, in addition (or as an alternative) to atraditional engine. For example, with respect to the vehicle 20, it maybe useful to provide one or more electric, hydraulic, or other energystorage devices as part of (or in communication with) the powertrain 22.Energy from the engine 24 may be received for storage at these devices(e.g., energy provided in mechanical form from the engine 24, thenconverted to non-mechanical forms for storage). The energy may then bereleased from storage for delivery to various vehicle components (e.g.,a transmission or other powertrain assembly), in various beneficialways.

In certain embodiments of the disclosed powertrain arrangement, an ESDsystem may be used to reduce the detrimental effects of transient powerevents for the vehicle 20. A transient power event may include events inwhich the power available from the engine 24 (at least under the currentoperating state of the engine 24) may be insufficient for one or moreongoing (or requested) operations. A transient power event may occur,for example, when a powered operation is requested by an operator, butthe available (i.e., surplus) power from the engine 24 (at least atcurrent operating conditions) is insufficient to complete the operationwithout detrimental effects (e.g., without reducing power supply toother vehicle systems). For example, while the engine 24 is activelypowering various vehicle systems (e.g., a set of drive wheels), anoperator may request an operation requiring additional power beyond thatcurrently available from the engine 24. In certain embodiments, an ESDsystem may be utilized to supplement (or replace) available engine powerfor such an operation, while avoiding various issues (e.g., power lags,inefficient engine operation, jerking of the vehicle 20, and so on).

A transient power event may also occur, for example, when an engine isproviding no power to the relevant powertrain. In certain embodiments,an ESD system may be utilized to provide power to various vehiclesystems when an engine is in a shut off state, or is otherwise notoperating.

In certain embodiments, a component of an IVP (e.g., an electricgenerator or hydraulic pump) may be configured to receive mechanicalpower from the engine 24 and convert the power to a different form(e.g., electrical power or hydraulic pressure/flow). A portion of theconverted power may be routed to an energy storage device (e.g., abattery or accumulator) for storage. As needed (i.e., during aparticular transient power event), stored energy may be then be releasedfrom the energy storage device to a component of the IVP (e.g., anelectric motor or hydraulic motor) for conversion back to mechanicalpower. This mechanical power may then be routed through the vehicle 20,as needed. For example, an MIVT may be configured to receive power fromthe IVP, to supplement mechanical power received directly from theengine 24.

In certain implementations, an ESD system in the disclosed powertrainarrangements may be utilized to provide shift smoothing. During certainshift events of a transmission of the vehicle 20 (e.g., duringtransition from a first range or gear of a multi-stage transmission to asecond range or gear of the multi-stage transmission) more power may bedemanded at an input to the transmission than is available from theengine 24 (i.e., a transient power event may occur). For example, one ormore clutches of the transmission may slip as the transmission begins toassume a post-shift-event load (e.g., an increased load). This slippagemay result in power consumption within the transmission itself (e.g.,due to the energy loss as the clutch slips), even as power istransmitted through the transmission to the transmission output. Assuch, the power required at the transmission input may be significantlylarger than the power available at the transmission output.

As a result of this power loss (or other factors), various adverseevents may occur with respect to the engine 24, the transmission, orother vehicle systems. For example, due to the excess power demand atthe transmission input, the engine 24 may temporarily “droop” or sufferother reduced performance, which may be perceived by a user as ahesitation of the vehicle 20 (or of the engine 24). Similarly, thetransmission may execute a sub-optimal shift, which may be perceived bya user as a jerking, stuttering, or even stalling of the vehicle 20.

Shift smoothing, as provided by an ESD system, may help to address these(and other) issues. For example, during steady (or other) operation ofthe vehicle 20, a portion of the power from the engine 24 may be routedto the ESD system (e.g., via an IVP) for storage (e.g., as storedelectrical, hydraulic, kinetic, or other energy). During a shift event,as appropriate, the ESD system may then deliver a portion of the storedenergy to the relevant transmission (e.g., via the IVP) in order tosupplement the power provided directly by the engine 24. In this way,even if a shift event causes a power demand at a transmission thatexceeds the (present) power output of the engine 24, power delivery fromthe ESD system may allow relatively smooth shifting operations. This maybe useful, for example, in order to avoid the need to increase enginespeed during shifting. Further, the use of an ESD system for shiftsmoothing may reduce the need for complex transmission designs (andcontrols), which might otherwise be necessary to provide smooth shiftsacross a variety of shift events.

An ESD system may provide various other benefits, in addition (or as analternative) to shift smoothing. In certain embodiments, an ESD systemmay be utilized for load leveling, in which increases in demand forpower during operations other than shift events may be met (at least inpart) with stored energy from the ESD system, rather than with increasedpower delivery from the engine 24. In certain implementations, this mayallow the engine 24 to be operated at a relatively constant load andrelatively constant speed during a wide range of operations of thevehicle 20, which may in turn result in more efficient utilization of agiven configuration of the engine 24. Likewise, an ESD system may beutilized to power operation of the vehicle 20 (or a sub-system thereof)without any ongoing power delivery from the engine 24. For example, in a“pure” electric (or hydraulic) mode, where the engine 24 may not beproviding any power for operation of the vehicle 20, an ESD system maypower operation of various vehicle systems, using previously-storedenergy.

In certain embodiments, an ESD system may be included in, or mayotherwise interface with, an IVP of the vehicle 20. For example, an IVPof the vehicle 20 may include a first IVP machine configured as anelectric generator or hydraulic pump, which may be configured to receivemechanical power from the engine 24 and convert the power, respectively,to electrical or hydraulic (or other) form. A battery or accumulator (orother energy storage device) may be in communication with the first IVPmachine such that a portion (i.e., part or all) of the converted powermay be routed to the battery or accumulator for storage. A second IVPmachine of the IVP (e.g., an electric motor or hydraulic motor) may beconfigured to receive power from the battery or accumulator (or directlyfrom the first IVP machine), and convert the received power tomechanical form for downstream components of the vehicle powertrain 22.

An ESD system may be controlled in various ways. In certain embodiments,the routing of power to and from an ESD system may be regulated using acontroller configured as a computing device of various designs (e.g., aprocessor and memory architecture, a programmable electronic circuit,and so on). In certain embodiments, for example, operation of an ESDsystem (as part of the disclosed powertrain arrangement) may beregulated by the TCU 36 or may be regulated by a different controller(not shown). An ESD system may be controlled based upon various inputs,including inputs from speed sensors (not shown) for the engine or othervehicle components, inputs from sensors (not shown) relating to shiftoperations, vehicle power consumption or demand, or inputs from variousother devices (not shown).

Referring also to FIG. 9, an example powertrain arrangement including anESD system is depicted. The powertrain of FIG. 9 is configured totransmit mechanical power from an internal combustion engine 24 d tovarious vehicle components and systems. As depicted, mechanical powerfrom the engine 24 d is routed along a shaft S8 to a planetary gear set48 d and a double planetary gear set 50 d, as well as to an electricgenerator 230. (It will be understood that, in other configurations, adifferent IVP machine may be utilized in place of, or in addition to,the generator 230.) The generator 230 is in electrical communicationwith a battery 234 (or other storage device for electric energy) andwith an electric motor 232. Collectively, the generator 230 and motor232 may be viewed as an IVP 28 d, in communication with an ESD system228 that includes the battery 234 (or batteries 234, as appropriate) aswell as various other components (not shown), including various powerelectronics, controllers, and so on.

The planetary gear set 48 d and double planetary gear set 50 d, as wellas the IVP 28 d, is configured to operate in a similar fashion to theplanetary gear set 48, double planetary gear set 50, and IVP 28 a ofFIG. 3 (as discussed in detail above), in order to provide an MIVT 26 dwith similar functionality to the MIVT 26 a. The MIVT 26 d may exhibitvarious differences, however. For example, in FIG. 9, it can be seenthat a shaft S16 is configured to receive power from the shaft S8 viathe drive gear for the generator 230, in order to power rotation of anauxiliary drive pulley 250. Likewise, a shaft S10 powered by a gear 44 dof the shaft S8 (which also provides power to the generator 230) mayprovide power to transmission control, scavenge, and other pumps.

During operation, power from the engine 24 d may be routed in variousways through the MIVT 26 d to a gear box 84 d (e.g., configured as acontrollable gear box), in order to provide infinitely variable,multi-mode power transmission to various vehicle systems. As depicted,for example, an output gear 82 d of the double planetary gear set 50 dis configured to mesh with input gears 236 and 238 of the gear box 84 d.Through the selective operation of clutches 252, the output gear 82 dmay accordingly power rotation of one of the transmission shafts S11 andS13, respectively. Selective control of various other clutches 254 maybe utilized to shift the gear box 84 d among various range gears 240,242, 244, 246 and 248, which may correspond, respectively, to ranges Athrough E for the gear box 84 d. In this way, power may be routed fromthe engine 24, as well as from the motor 232, to the differential driveshaft S12 a. Also as depicted, a brake 256 and clutch 258 may becontrolled to transmit power from the gear box 84 d to a drive shaft S12b for mechanical front wheel drive. (It will be understood that thedepicted configuration of the various gears of the gear box 84 d ispresented as an example only. An ESD system may also be utilized withregard to other configurations of the gear box 84 d).

Other devices and functionality may also be provided. For example, itcan be seen that the gear 44 d of the shaft S8 is configured to rotatean idler gear 68 d on the shaft S12 a, as well as to provide power tothe generator 230. In turn, the gear 68 d may power rotation of a PTOshaft S14 and, in certain configurations, a front PTO shaft S15.

As regulated by an appropriate controller (not shown), a portion of thepower received at the generator 230 may be routed, once converted toelectrical form, to the ESD 228 for storage in the battery 234. Incertain implementations, power may be routed from the generator 230 tothe battery 234 continuously, as long as the engine 24 d is running andthe battery 234 is not fully charged. In certain implementations, powermay be routed from the generator 230 to the battery 234 moreselectively. For example, under certain control strategies, power may berouted from the generator 230 to the battery 234 only when it has beendetected (e.g., via various engine or other sensors (not shown)) thatthe engine 24 d is producing surplus power with regard to the currentpower demands of vehicle operation.

As needed, energy may be released from the battery 234 to poweroperation of the motor 232. As described above, with regard to motor 42of FIG. 3, power from the motor 232 may then be routed through thedouble planetary gear set 50 d in order to supplement (or replace) powerfrom the engine 24 d. This may be useful, for example, in order toensure that appropriate power is provided to the various systems anddevices of the vehicle 20, even while the engine 24 d is maintained atan optimal, and relatively constant operating speed.

In certain implementations, power from the battery 234 may be utilized,via the motor 232, for shift smoothing operations. For example, during(or before or after) a shift from the A-range gear 240 to the B-rangegear 242, a relevant controller may identify that additional power maybe required at the gear box 84 d in order to ensure a smooth shift and,in certain embodiments, to avoid the need to increase engine speed orpower. Accordingly, for the A-to-B shift event (and other shift events),energy may be released from the battery 234 to the motor 232, such thatthe motor 232 may provide additional power to the gear box 84 d (i.e.,via the double planetary gear set 50 d).

Shift smoothing, such as in the example described above, may beimplemented based upon a variety of factors. In certain implementations,for example, a signal from the TCU 36 (or other device) may indicatethat a shift between gears of the gear box 84 d is about to occur (or isoccurring or has recently occurred). Where such a shift event isidentified as (or expected to) result in a transient power event, powermay be routed from the ESD 228 accordingly. In certain implementations,engine sensors, shaft speed sensors, or other sensors (not shown) maydetect indications of a power deficiency at the gear box 84 d (e.g., dueto clutch slippage within the gear box 84 d during a shiftingoperation). Routing of power from the ESD 228 to the gear box 84 d maythen be implemented accordingly.

In certain implementations, power from the battery 234 may be utilizedfor other operations. For example, where operation of the engine 24 dmay not be possible or practical (e.g., during operation of the vehicle20 within an enclosed space), energy from the battery 234 may beutilized to implement electric-only operation of the vehicle 20. Incertain implementations, electric-only operation may be implementedautomatically (e.g., based upon receiving a drive or other command whenthe vehicle is keyed on, but the engine 24 d is off). In certainimplementations, electric-only operation may be implemented based uponother factors (e.g., based upon an operator toggling a particularswitch, button, or lever).

As another example, where use of a particular vehicle tool imposesincreased power demands on the vehicle 20, energy from the battery 234may be utilized to ensure that appropriate power is available at thetool, without significantly adverse effect on the operation of othervehicle systems (e.g., the vehicle drive wheels) or a significantincrease in engine speed. For example, where a mechanical tool (e.g., abaling device, seeding device, soil-conditioning device, cutting blade,and so on) is being driven by the PTO shaft S14, or a hydraulic tool(e.g., a loading bucket, dump truck bed, excavator arm,soil-conditioning device, and so on) is being operated using power fromthe front PTO shaft S15 or another shaft (i.e., as converted by anappropriate hydraulic pump (not shown)), the drive train of the vehicle20 may be subjected to increased power demands. In certain embodiments,accordingly, during operation of such a tool, energy from the battery234, as converted to mechanical energy by the motor 232, may be utilizedto supplement (or replace) power from the engine 24 d with respect tothe relevant tool (or other vehicle systems).

In certain implementations, power from the battery 234 may be utilizedautomatically, whenever any vehicle tool (or any vehicle tool ofparticular configuration) is operated. In certain implementations, powerfrom the battery 234 may be utilized more selectively. For example,engine sensors, shaft speed sensors, or other sensors (not shown) maydetect indications of a power deficiency due to tool operation, andpower may be drawn from the battery 234 appropriately.

Referring also to FIG. 10, another example MIVT 26 e is configuredsimilarly to the MIVT 26 c of FIG. 7. An internal combustion engine 24 eprovides mechanical power via a shaft S17 to a double planetary gear set178 e as well as to an electric generator 172 e (or other IVP machine)included in an IVP 28 e. The generator 172 e converts the mechanicalpower from the engine 24 e to electrical power, which is routed to anelectric motor 174 e. The motor 174 e then converts the electrical powerto mechanical power, which is also routed to the double planetary gearset 178 e. In this way, the MIVT 26 e, via the double planetary gear set178 e, may be utilized to combine power from the engine 24 e and the IVP28 e, in order to provide continuously variable power to a transmission202 e.

In the embodiment depicted, the generator 172 e is in electricalcommunication with a battery 260 (or other storage device for electricenergy), as well as with the motor 174 e. In this way, mechanical energyfrom the engine 24 e may be stored as electrical energy in the battery260, and released, as appropriate, via the motor 174 e, to provide powerto the double planetary gear set 178 e. As described in detail withrespect to the configuration of FIG. 9, energy from the battery 260 maybe utilized to provide shift smoothing, to operate the vehicle 20 in anelectric-only mode, to power operation of a tool of the vehicle 20 (orto power other vehicle systems during operation of such a tool), and soon.

It will be understood that the various storage devices of an ESD system(e.g., the batteries 234 and 260) may receive and store energy fromsources other than the relevant engine (e.g., the engines 24 d and 24e). For example, in certain implementations, regenerative systems (e.g.,systems for capturing energy from braking operations) may be configuredto route power to an ESD system for later use (e.g., for shiftsmoothing, electric-only operation, and so on) or may form part of anESD system. Likewise, it will be understood that an ESD system may beutilized with powertrains and transmissions (including MIVTs) other thanthose specifically depicted. In certain embodiments, for example, an ESDsystem (not shown) may be implemented with respect to the powertraindepicted in FIG. 5 via a hydraulic accumulator 264 (see FIG. 5,hydraulic connections not shown), or with respect to various otherpowertrain configurations (not shown).

Various of the operations described above (and others) may beimplemented as part of a transient power event management (“TPEM”)method. Referring also to FIG. 11, for example, a TPEM method 300 may beimplemented for the vehicle 20 by various controllers (e.g., the TCU 36)or other devices.

The TPEM method 300 may include identifying 302 a transient power event.For example, by way of an engine speed sensor, various shaft speedsensors, other sensors or devices, a controller may identify 302 that acurrent (or imminent) operating state of the relevant vehicle hasresulted (or is likely to result) in a power deficiency. For example, ashift operation 304 (e.g., a, recent, ongoing, or imminent shiftoperation 304) may be identified 302, during which a transmission maydemand more power from an engine (e.g., due to clutch slippage) than maybe available from the engine (at least in the current operating state).For example, due to clutch slippage during a shift event, more power maybe demanded from the engine at the input to a transmission than isavailable from the engine at the current engine speed. Similarly,operation 306 of a tool (e.g., an ongoing or imminent operation 306 ofthe tool) may be identified 302, during which the power requirements ofthe tool (e.g., in combination with other power requirements for othervehicle systems) may exceed the available power from the engine. Incertain implementations, identifying 302 a transient power invent mayinclude identifying 302 the operation of the vehicle (or a subsystemthereof) while the engine is in a shut off (or otherwise un-powered)state 308. For example, a drive operation or the operation of a vehicletool (e.g., an ongoing or imminent drive or tool operation) may beidentified 302 while the engine is in a shut off state 308.

The method 300 may further include causing 320 an energy storage device(e.g., as may form part of a larger ESD system) to provide stored energyto a component of an IVP (e.g., an IVP machine). For example, the method300 may be utilized to cause 320 energy from a battery to be provided toan electric motor, to cause 320 energy from a hydraulic accumulator tobe provided to a hydraulic motor, and so on. (In certainimplementations, it will be understood that this may be preceded by themethod 300 causing 322 energy to be stored in the IVP. In certainimplementations, energy may be stored in the IVP in other ways.)

The method 300 may then include providing 330 power from the componentof the IVP (e.g., from an IVP machine) to a transmission. For example,the method 300 may include providing 330 power from an electric orhydraulic motor to an MIVT of various configurations, to a transmissionwith fixed gear ratios, or to other transmissions included in therelevant powertrain.

In certain implementations, the method 300 may further include providing340 power to the transmission from the engine. For example, where theengine is not in a shut-off state 308, an MIVT (or other device) may beutilized to sum the power received, respectively, from the engine andfrom the IVP, such that power from both the engine and the IVP may beprovided 330, 340 to the relevant transmission.

Referring now to FIGS. 12-16, the present disclosure will be discussedaccording to additional example embodiments. It should be noted that theschematic representations of the powertrains shown in FIGS. 12, 14, 15,and 16 illustrate example implementations in simplified form forclarity, and thus may not depict all of the components associated withthe represented powertrain.

As will be discussed, the powertrain of the present disclosure providesa multi-mode infinitely variable transmission (IVT). The IVT providessplit-path power transmission, combining power from an engine and atleast one infinitely variable power (IVP) machine. For example, thepowertrain may include an engine, a first electrical machine, and asecond electrical machine.

As mentioned above, it may be useful to facilitate a powered-zero modefor a vehicle (or other machinery), in which the output speed of thevehicle wheels (or other machinery output) reaches zero speed withoutstopping the engine or releasing torque at the wheels. In this way, forexample, vehicle power may be utilized to hold a vehicle stationary.Such a state may be obtained, for example, with a planetary gearset. Forexample, if an engine is spinning a sun gear at a first positive speedand an IVP machine (e.g., an electric motor powered by a generator) isdirected to spin a ring gear at an equivalent negative speed, anassociated planet gear carrier (which may, for example, be connected toa differential drive shaft) may not spin at all. Further, if the IVPprovides an output rotation at a slightly different (and opposite) speedfrom the engine, the vehicle may enter a “creeper” mode, in which thevehicle moves very slowly but with high wheel torque. The powered-zeroand creeper modes are particularly useful for heavy-duty work vehicles,such as the tractor shown in FIG. 1, used in the agricultural,construction and forestry industries. With increasing wheel speed, thevehicle may then, eventually, enter a normal drive mode (i.e., “fieldmode”).

As will be discussed, in at least one mode of the IVT of the presentdisclosure, split-path power transmission may be provided wherein thepowered-zero state can be achieved. Split-path power transmission maycontinue as the speed of the vehicle increases from the powered-zerostate, into the creeper mode(s). Moreover, in at least one mode, thefirst IVP machine and a second IVP machine may co-generate electricityto satisfy electrical demands. The IVP machines may co-generate when thevehicle is in the powered-zero state and as the vehicle speed increasestherefrom into the creeper mode(s). Thus, the vehicle may be useful forperforming a wide variety of work while simultaneously satisfying highelectrical demands of various electrical components.

Additionally, the IVT may be configured in a variety of ways, whereinthe above-described split-path, powered zero with electricalco-generation capability may be an optional feature for a particularIVT. Accordingly, the IVT may be modular and configurable. Stateddifferently, the IVT may have a first configuration (e.g., FIG. 12) inwhich the IVT provides split-path, powered-zero, co-generationcapability, and a second configuration (e.g., FIG. 14) in which the IVTdoes not provide this capability. Accordingly, the transmission may beconfigured according to the type of work to be performed by the vehicle,according to space constraints within the vehicle, or otherwise.

The example embodiment illustrated in FIG. 12 will now be discussed indetail. As shown in FIG. 12, a powertrain 22 may include an engine 502,such as an internal combustion engine. The engine 502 may providemechanical power directly to an engine shaft 509.

The powertrain 22 may additionally include an infinitely variable power(IVP) source 501, which may include at least one IVP machine. As shownin the illustrated embodiment, the IVP source 501 may include a firstIVP machine 504 and a second IVP machine 506. In some embodiments, thefirst IVP machine 504 may comprise a first electric machine 503, and thesecond IVP machine 506 may include a second electric machine 505.

The powertrain 22 may further include a multi-mode infinitely variabletransmission (MIVT), which is generally indicated at 515. The MIVT 515may transmit mechanical power among the engine 502, the first electricmachine 503, and the second electric machine 505 as will be discussed indetail below. The MIVT 515 may also transmit power to an output shaft507. Power may be transmitted through the MIVT 515 along differentpaths, depending on the current transmission mode of the MIVT 515. Thevehicle (e.g., the tractor of FIG. 1 or another work vehicle) mayinclude wheels that are rotatably driven by the output shaft 507 (e.g.,via one or more differentials).

As will be discussed, the first electric machine 503 may switch betweena generator mode and a motor mode. In the generator mode, the firstelectric machine 503 may receive mechanical energy from the MIVT 515 andconvert it into electrical energy that can be supplied to the secondelectric machine 505 and/or an implement 521. Conversely, in the motormode, the first electric machine 503 may convert electric energy intomechanical energy that is supplied to the MIVT 515.

Likewise, the second electric machine 505 may switch between a motormode and a generator mode. In the motor mode, the second electricmachine 505 may convert electric energy into mechanical energy that issupplied to the MIVT 515. Conversely, in the generator mode, the secondelectric machine 505 may receive mechanical energy from the MIVT 515 andconvert it into electrical energy that can be supplied to the firstelectric machine 503 and/or the implement 521.

The implement 521 may be a seeding implement, a shovel, a bucket, orother device. In some embodiments, the implement 521 may be powered byelectrical energy supplied, at least in part, by the IVP 501. Also, theimplement 521 may be mounted on-board the vehicle or may be remote andtethered to the vehicle, at least, by power cables.

The MIVT 515 may include a first planetary gearset 508. The firstplanetary gearset 508 may be a double planetary gearset including aplurality of transmission components. For example, the double planetarygearset may include a first sun gear 510, a first ring gear 512, aplurality of first planet gears 514 with an associated carrier 525, asecond sun gear 516, a second ring gear 518, and a plurality of secondplanet gears 520 with an associated carrier 527. In some embodiments,the first sun gear 510, first ring gear 512, and first planet gears 514may collectively comprise a so-called “LO gearset” of the firstplanetary gearset 508, and the second sun gear 516, second ring gear518, and second planet gears 520 may collectively comprise a so-called“HI gearset” of the first planetary gearset 508. Also, the second ringgear 518 may be directly engaged for rotation with the carrier 525 ofthe first planet gears 514 in some embodiments.

The MIVT 515 may additionally include a second planetary gearset 522.The second planetary gearset 522 may be a single planetary gearsetincluding a plurality of transmission components. For example, thesingle planetary gearset may include a sun gear 524, a ring gear 526,and a plurality of planet gears 528 with an associated carrier 529.

As will be discussed, in at least one mode of the MIVT 515, the powerand torque output of the first planetary gearset 508 may be input to thesecond planetary gearset 522, and the second planetary gearset 522 may,in turn, provide power and/or torque to the output shaft 507 of thevehicle. In some embodiments, the powertrain 22 may provide powered-zeroand/or creeper modes in this fashion.

The MIVT 515 may include a plurality of transmission components (e.g.,gears, shafts, etc.) that is interconnected to transmit mechanical powerthrough the MIVT 515. These components may be configured to transmitpower among the engine 502, the first electric machine 503, the secondelectric machine 505, and ultimately to the output shaft 507. One ormore of these transmission components may define a “transmissionbranch”. In some embodiments, a first transmission branch may transmitpower between the engine 502 and the first planetary gearset 508.Likewise, in some embodiments, a second transmission branch may transmitpower between the first planetary gearset 508 and the second planetarygearset 522. Furthermore, in some embodiments, a third transmissionbranch may transmit power between the second planetary gearset 522 andthe output shaft 507, and so on, as will be explained in detail below.

One or more transmission branches of the MIVT 515 may comprise a seriesof interconnected and/or enmeshed gears. The gears may be spur gears,bevel gears, or other types of gears. Also, two gears within aparticular transmission branch may be enmeshed together (e.g., withparallel but spaced-apart axes of rotation). Furthermore, two gearswithin a particular transmission branch may be engaged for rotation witheach other, and interconnected via a shaft(s) (e.g., with one or moreshafts that are co-axial with the two gears in question).

In some embodiments, two shafts within a particular transmission branchmay be engaged for rotation with each other and, alternatively,disengaged from each other. For example, a clutch may be included in thetransmission branch and interposed between the two shafts. In a clutchedposition, the two shafts may be engaged for rotation with each other. Inan unclutched position, the two shafts may be disengaged for independentrotation.

As shown in FIG. 12, the MIVT 515 may include a plurality of clutches569. In some embodiments, the plurality of clutches 569 of the MIVT 515include a first clutch 570, a second clutch 572, a third clutch 574, afourth clutch 576, a fifth clutch 578, a sixth clutch 580, and seventhclutch 582. Each of these clutches 569 may operate independently and mayactuate between a clutched position (i.e., engaged position, energizedposition, etc.) and, alternately, an unclutched position (i.e.,disengaged position, deenergized position, etc.). In some embodiments,the clutches 569 are operably connected to respective ones of thetransmission branches.

Different transmission branches of the MIVT 515 may transmit power at agiven time depending on the mode of the MIVT 515. For each transmissionmode, a predetermined subset of the plurality of clutches 570, 572, 574,576, 578, 580, 582 may be engaged while the others may be disengaged.Different subsets of the clutches 570, 572, 574, 576, 578, 580, 582 maybe engaged in the different modes. This allows power to be routedthrough the MIVT 515 in a variety of ways to supply the mechanical andelectrical demands of the vehicle.

The different transmission modes of the MIVT 515 will now be discussed.FIG. 13 illustrates these different transmission modes according to anexample embodiment of the present disclosure. Specifically, FIG. 13illustrates a relationship between the wheel speed of the vehicle(X-axis) and the rotational speed of the second electric machine 505(Y-axis). In some embodiments, the MIVT 515 may provide a first mode(represented by line 584 in FIG. 13), a second mode (represented by line586), a third mode (represented by line 588), a fourth mode (representedby line 590), a fifth mode (represented by line 592), and a sixth mode(represented by line 594). These modes may represent forward modes ofthe vehicle, wherein the vehicle moves forward from a stationaryposition. The MIVT 515 may also include additional modes, such as atleast one reverse mode, wherein the vehicle moves in the opposite,reverse direction from a stationary position.

In the first mode of the MIVT 515, the first clutch 570, the fourthclutch 576, and the fifth clutch 578 may be in the clutched position,and the other clutches 572, 574, 580, 582 may be in the unclutchedposition. As such, power (i.e., engine power) may be transmitted along afirst transmission branch from the engine shaft 509 to the carrier 527of the second planet gears 520 of the first planetary gearset 508. Morespecifically, power may be transmitted through this first transmissionbranch, from the engine shaft 509, through the first clutch 570, andthrough the fourth clutch 576 to a gear 536. The gear 536 is meshed witha gear 540, which is attached to the carrier 527 of the second planetgears 520. This first transmission branch may be a one-way powertransmission path from the engine shaft 509 to the second planet gears520 in some embodiments.

Additionally, in the first mode of the MIVT 515, a second transmissionbranch may be defined between the first electric machine 503 and theengine shaft 509 for transmission of power (i.e., IVP powertransmission) therebetween. The second transmission branch may include agear 546 that is engaged for rotation with a shaft of the first electricmachine 503. The gear 546 may be enmeshed with a gear 548 that ismounted on opposite ends of a co-axial shaft with a gear 550. The gear550 may be enmeshed with a gear 530. This second transmission branch maybe a two-way power transmission path between the first electric machine503 and the engine shaft 509. In other words, the first electric machine503 may either: (a) operate in generator mode, receiving power from thegear 546 and converting it into electrical energy for supplying theimplement 521, the second electric machine 505 or otherwise; or (b)operate in motor mode, supplying power to the gear 546 and, ultimatelyback to the first transmission branch discussed above. The direction ofpower transmission through this transmission branch may be controlled,for example, by controlling first electric machine 503 in someembodiments (i.e., by controlling the speed and rotation direction ofthe gear 546).

Also, in this first mode of the MIVT 515, a third transmission branchmay be defined between the second sun gear 516 and the second electricmachine 505 for transmission of power (i.e., IVP power transmission)therebetween. More specifically, power may be transmitted in eitherdirection between the second sun gear 516 and the second electricmachine 505 via a gear 554 and a gear 552, which are enmeshed with eachother. As shown in FIG. 12, the gear 554 is engaged for rotation withthe second sun gear 516, and the gear 552 is engaged for rotation withthe second electric machine 505. This third transmission branch may be atwo-way power transmission path between the second sun gear 516 and thesecond electric machine 505, meaning that the second electric machine505 may either: (a) operate in motor mode and supply power toward thesecond sun gear 516; or (b) operate in generator mode, receivingmechanical power and converting it into electrical power that may besupplied to the first electric machine 503, the implement 521, or otherelectric power consumer. The direction of power transmission throughthis transmission branch may be controlled, for example, by controllingsecond electric machine 505 in some embodiments (i.e., by controllingthe speed and rotation direction of the gear 552).

Additionally, a fourth transmission branch may be defined between thesecond ring gear 518 and the sun gear 524 of the second planetarygearset 522. More specifically, power (i.e., combined power) may betransmitted from the second ring gear 518, through the first planetgears 514, to a gear 556, which is enmeshed with a gear 557, which isenmeshed with a gear 558, and which is enmeshed with a gear 560. Thegear 560 may be engaged for rotation with the sun gear 524 of the secondplanetary gearset 522. This fourth transmission branch may be a one-waypower transmission path from the second ring gear 518 and the sun gear524.

A fifth transmission branch in this first transmission mode may bedefined from the ring gear 526 of the second planetary gearset 522 tothe engine shaft 509. More specifically, power may be transmittedthrough this fifth transmission branch, from the ring gear 526, to agear 531 that is engaged for rotation to the ring gear 526. The gear 531may be engaged with a gear 532, and power may be transmitted from gear532 back to the engine shaft 509. The gear 532 may be considered aflywheel. This fifth transmission branch may be a one-way powertransmission path from the ring gear 526 to the engine shaft 509 in someembodiments.

Moreover, a sixth transmission branch may be defined from the planetgears 528 of the second planetary gearset to the output shaft 507. Morespecifically, power may be transmitted from the planet gears 528,through the clutch 578, to gear 542, which is enmeshed with gear 544,which is engaged for rotation with the output shaft 507. This sixthtransmission branch may be a one-way transmission path from the planetgears 528 to the output shaft 507.

It will be appreciated that, in this first transmission mode, the firstplanetary gearset 508 and the second planetary gearset 522 both providea split-path for power transmission within the MIVT 515. The firstplanetary gearset 508 combines input from the engine 502 andinput/output of the second electric machine 505 such that output of thefirst planetary gearset 508 (i.e., first combined power) is input to thesecond planetary gearset 522. Also, the second planetary gearset 522combines input from the first planetary gearset 508 and output to theengine shaft 509 such that output of the second planetary gearset 522(i.e., second combined power) is output to the output shaft 507.

Furthermore, powered-zero may be achieved in this first transmissionmode of the MIVT 515. Specifically, the combination at the secondplanetary gearset 522 may include the sun gear 524 receiving power inputfrom the first planetary gearset 508 and the ring gear 526 outputtingpower toward the engine shaft 509, resulting in the carrier 529 of theplanet gears 528 remaining stationary (i.e., zero rpm) while maintainingtorque at the output shaft 507. Additionally, as shown in FIG. 13, thespeed of the second electric machine 505 may be increased in the firstmode to increase the wheel speed of the vehicle from the powered-zerostate (i.e., creeper mode).

Additionally, in some embodiments, the first electric machine 503 andthe second electric machine 505 may co-generate electricitysimultaneously while in the powered-zero state and in the creeper mode.In the example of FIG. 13, for example, the powered-zero state may berepresented at point 596, wherein the gear 552 of the second electricmachine 505 is rotating in a first direction. The speed of the vehiclemay be increased by decreasing the speed of the gear 552. In someembodiments, the second electric machine 505 may generate power from thepowered-zero state (point 596) to the point at which the output speed ofthe gear 552 equals zero (point 598). At the same time, the firstelectric machine 503 may be in generator mode as well.

Assuming that the speed of the gear 552 begins rotating in the oppositedirection and increases therefrom (from point 598 to point 600), thesecond electric machine 505 may enter motor mode such that the secondelectric machine 505 supplies power to the gear 552.

The second transmission mode is represented by line 586 in FIG. 13according to example embodiments. In the second mode of the MIVT 515,the first clutch 570, the third clutch 574, and the fifth clutch 578 maybe in the clutched position, and the other clutches 572, 576, 580, 582may be in the unclutched position. As such, power may be transmittedalong a first transmission branch from the engine shaft 509 to the firstring gear 512 of the first planetary gearset 508. More specifically,power may be transmitted through this first transmission branch, fromthe engine shaft 509, through the first clutch 570, and through thethird clutch 574 to a gear 534. The gear 534 is meshed with a gear 538,which is attached to the ring gear 512. This first transmission branchmay be a one-way power transmission path from the engine shaft 509 tothe ring gear 512 in some embodiments.

Additionally, in this second transmission mode, the second transmissionbranch between the first electric machine 503 and the gear 530 may besubstantially the same as discussed above.

Furthermore, the third transmission branch may be defined between thesecond electric machine 505 and the first sun gear 510 of the firstplanetary gearset 508. More specifically, power may be transmitted ineither direction between the first sun gear 510 and the second electricmachine 505 via enmeshed gear 552 and gear 554. This third transmissionbranch may be a two-way power transmission path between the first sungear 510 and the second electric machine 505, meaning that the secondelectric machine 505 may either: (a) operate in motor mode and supplypower toward the sun gear 510; or (b) operate in generator mode,receiving mechanical power and converting it into electrical power thatmay be supplied to the first electric machine 503, the implement 521, orother electric power consumer.

Additionally, a fourth transmission branch may be defined between thecarrier 525 of the first planet gears 514 and the sun gear 524 of thesecond planetary gearset 522. More specifically, power may betransmitted from the first planet gears 514, to a gear 556, which isenmeshed with a gear 557, which is enmeshed with a gear 558, and whichis enmeshed with a gear 560. The gear 560 may be engaged for rotationwith the sun gear 524 of the second planetary gearset 522. This fourthtransmission branch may be a one-way power transmission path from thesecond ring gear 518 to the sun gear 524.

Moreover, a fifth transmission branch in this second transmission modemay be defined from the ring gear 526 of the second planetary gearset522 to the engine shaft 509. This fifth transmission branch may beconfigured as discussed above with relation to the first transmissionmode.

Also, a sixth transmission branch may be defined from the planet gears528 of the second planetary gearset to the output shaft 507. Morespecifically, power may be transmitted from the planet gears 528,through the clutch 578, to gear 542, which is enmeshed with gear 544,which is engaged for rotation with the output shaft 507. This sixthtransmission branch may be a one-way transmission path from the planetgears 528 to the output shaft 507.

With reference to FIG. 13, the first and second electric machines 503,505 may co-generate when the MIVT 515 is in this second transmissionmode. This co-generation may occur when the speed of the gear 552 ofsecond electric machine 505 is at speed represented by point 602 and asthe speed of the gear 552 reduces toward zero at point 604. Then, as thespeed of the gear 552 increases in the opposite direction, the secondelectric machine 505 may enter the motor mode.

It will be appreciated that the second electric machine 505 may remainin the generator mode from the powered-zero state in the firsttransmission phase through the lower output speed range of the secondtransmission phase (e.g., from point 596 to point 604 in FIG. 13). Inone example sequence, the MIVT 515 may be in the powered-zero state (atpoint 596), and the MIVT 515 may remain in the first transmission modeas the wheel speed of the MIVT 515 increases. At point 598, the secondelectric machine 505 may remain in the generator mode by shifting theMIVT 515 into the second transmission phase (i.e., shift to point 602).The MIVT 515 may remain in the second transmission mode as the outputspeed increases. Accordingly, as shown in FIG. 13, there is sufficientoverlap between the first transmission mode and the second transmissionmode such that the second electric machine 505 may continuously remainin the generator mode from the first transmission mode to the secondtransmission mode.

The third transmission mode (i.e., first field mode) of the MIVT 515 maybe represented by line 588 in FIG. 13. In the third transmission mode,the first clutch 570, the third clutch 574, and the sixth clutch 580 maybe in the clutched position, and the other clutches 572, 576, 578, 582may be in the unclutched position. As such, power may be transmittedalong a first transmission branch from the engine shaft 509 to the firstring gear 512 of the first planetary gearset 508. More specifically,power may be transmitted through this first transmission branch, fromthe engine shaft 509, through the first clutch 570, and through thethird clutch 574 to a gear 534. The gear 534 is meshed with a gear 538,which is attached to the ring gear 512. This first transmission branchmay be a one-way power transmission path from the engine shaft 509 tothe ring gear 512 in some embodiments.

Additionally, in this third transmission mode, the second transmissionbranch between the first electric machine 503 and the gear 530 may besubstantially the same as discussed above with respect to the first andsecond transmission modes.

Furthermore, the third transmission branch between the second electricmachine 505 and the first sun gear 510 may be substantially the same asdiscussed above with respect to the second transmission mode.

Moreover, the first planetary gearset 508 may combine power at the firstring gear 512 and the first sun gear 510 and output power from the firstplanet gears 514 to the output shaft 507. More specifically, in thisfourth transmission branch, power may be transmitted from the firstplanet gears 514, through the sixth clutch 580, to a gear 562, which isenmeshed with a gear 544. The gear 544 may be engaged for rotation withthe output shaft 507.

It will be appreciated that power transmission through the MIVT 515bypasses the second planetary gearset 522 in this third transmissionmode. In other words, power output from the first planetary gearset 508is transmitted directly to the output shaft 507.

Also, it will be appreciated that the second electric machine 505 may bein generator mode from point 606 of FIG. 13 to point 608. Thus, assumingthat the MIVT 515 is in the second transmission mode, the output speedcontinues to increase, and electrical demand is still high enough, theMIVT 515 may shift from the second transmission mode to the thirdtransmission mode (i.e., by adjusting the speed of gear 552 from point604 to point 606 in FIG. 13).

The fourth transmission mode (i.e., second field mode) of the MIVT 515may be represented by line 590 in FIG. 13. In the fourth transmissionmode, the first clutch 570, the fourth clutch 576, and the sixth clutch580 may be in the clutched position, and the other clutches 572, 574,578, 582 may be in the unclutched position. As such, power may betransmitted along a first transmission branch from the engine shaft 509to the second planet gears 520 of the first planetary gearset 508. Morespecifically, power may be transmitted through this first transmissionbranch, from the engine shaft 509, through the first clutch 570, andthrough the fourth clutch 576 to gear 536. The gear 536 is meshed withgear 540, which is attached to the carrier 527 of the planet gears 520.This first transmission branch may be a one-way power transmission pathfrom the engine shaft 509 to the second planet gears 520 in someembodiments.

Additionally, in this fourth transmission mode, the second transmissionbranch between the first electric machine 503 and the gear 530 may besubstantially the same as discussed above with respect to the first,second, and third transmission modes.

Furthermore, the third transmission branch between the second electricmachine 505 and the second sun gear 516 may be substantially the same asdiscussed above with respect to the first transmission mode.

Moreover, the first planetary gearset 508 may combine power of thesecond planet gears 520 and the second sun gear 516 and output powerfrom the second ring gear 518 to the output shaft 507. Morespecifically, in this fourth transmission branch, power may betransmitted from the second ring gear 518, through the first planetgears 514, through the sixth clutch 580, to the gear 562, and ultimatelyto the gear 544 for rotating the output shaft 507.

The fifth transmission mode (i.e., third field mode) of the MIVT 515 maybe represented by line 592 in FIG. 13. In the fifth transmission mode,the first clutch 570, the third clutch 574, and the seventh clutch 582may be in the clutched position, and the other clutches 572, 576, 578,580 may be in the unclutched position. As such, power may be transmittedalong a first transmission branch from the engine shaft 509 to the firstring gear 512 of the first planetary gearset 508, similar to the firsttransmission branch defined in the first transmission mode.

Additionally, in this fifth transmission mode, the second transmissionbranch between the first electric machine 503 and the gear 530 may besubstantially the same as discussed above with respect to the first,second, and third transmission modes.

Furthermore, the third transmission branch between the second electricmachine 505 and the first sun gear 510 may be substantially the same asdiscussed above with respect to the second and third transmission modes.

Moreover, the first planetary gearset 508 may combine power of the firstring gear 512 and the first sun gear 510 and output power from thesecond planet gears 514 to the output shaft 507. More specifically, inthis fourth transmission branch, power may be transmitted from thecarrier 525 of the first planet gears 514 to the gear 556, which isenmeshed with the gear 557 for rotating the output shaft 507.

The sixth transmission mode (i.e., fourth field mode) of the MIVT 515may be represented by line 594 in FIG. 13. In the sixth transmissionmode, the first clutch 570, the fourth clutch 576, and the seventhclutch 582 may be in the clutched position, and the other clutches 572,574, 578, 580 may be in the unclutched position. As such, power may betransmitted along a first transmission branch from the engine shaft 509to the second planet gears 520 of the first planetary gearset 508,similar to the first transmission branch defined in the fourthtransmission mode.

Additionally, in this sixth transmission mode, the second transmissionbranch between the first electric machine 503 and the gear 530 may besubstantially the same as discussed above with respect to the first,second, third, fourth and fifth transmission modes.

Furthermore, the third transmission branch between the second electricmachine 505 and the second sun gear 516 may be substantially the same asdiscussed above with respect to the fourth transmission mode.

Moreover, the first planetary gearset 508 may combine power of thesecond planet gears 520 and the second sun gear 516 and output powerfrom the second ring gear 518 to the output shaft 507. Morespecifically, in this fourth transmission branch, power may betransmitted from the second ring gear 518, through the first planetgears 514, through the sixth clutch 580, to the gear 562, and ultimatelyto the gear 544 for rotating the output shaft 507.

The MIVT 515 may also include one or more reverse modes. The reversemodes may be similar to the first, second, third, fourth, fifth, andsixth reverse modes described above, except that the second clutch 572is clutched instead of the first clutch 570 in each mode.

Thus, as an example first reverse mode, the second clutch 572, thefourth clutch 576, and the fifth clutch 578 are clutched and the otherclutches 570, 574, 580, 582 remain unclutched. As such, power istransmitted from the engine shaft 509, through the second clutch 572(i.e., the reverser clutch), to the second planet gears 520 of the firstplanetary gearset 508. Specifically, power is transmitted from theengine shaft 509, to gear 530, which is enmeshed with gear 550, which isenmeshed with gear 568. This power is transferred through the secondclutch 572 to gear 531, which is enmeshed with the gear 532. This poweris transmitted through the fourth clutch 576 to gear 536, which isenmeshed with the gear 540, and ultimately to the second planet gears520. The other transmission branches may be the same as described abovewith respect to the first transmission mode. Other reverse transmissionmodes may be configured similarly (i.e., similar to the modes describedin detail below, except that the second clutch 572 is clutched insteadof the first clutch 570 in each).

Referring now to FIG. 14, certain modular features of the powertrain 22′and the MIVT 515′ will be discussed in detail. The powertrain 22′ andMIVT 515′ of FIG. 14 may have a modular configuration that is differentfrom the modular configuration of the MIVT 515 embodied in FIG. 12.

As shown, the MIVT 515′ may be substantially similar to the MIVT 515 ofFIG. 12, except the second planetary gearset 522 of FIG. 12 andassociated gears 542, 558, and 560, and the fifth clutch 578 may beomitted in the configuration of FIG. 14.

In some embodiments, the MIVT 515′ may have the third mode, the fourthmode, the fifth mode, and the sixth mode. These modes may correspond,respectively, to the third, fourth, fifth, and sixth modes as describedabove.

The first and second modes (powered-zero and creeper modes) as describedabove would be unavailable to the MIVT 515′ of FIG. 14. This is becausethe planetary gearset 508 combines the engine power provided by theengine 502 and the second MIVP 501 as discussed above. The combinedoutput power is transmitted from the gearset 508 directly to the outputshaft 507. This contrasts with the configuration of FIG. 12, wherein thecombined output power from the first planetary gearset 508 is deliveredto the second planetary gearset 522, which splits the input powerbetween the output shaft 507 and gear 532.

Thus, the modular configuration of the MIVT 515′ of FIG. 14 does notprovide the powered-zero, co-generation capabilities of the MIVT 515 ofFIG. 12. However, for some vehicles and/or some customers, thiscapability may not be necessary. Also, the modular configuration of FIG.14 may be more compact than that of FIG. 12 because it includes fewerparts. Thus, a first work vehicle may be built to include the modularconfiguration of FIG. 14, and a second work vehicle may be built toinclude the modular configuration of FIG. 12, depending on the type ofwork to be performed by the vehicle, the space constraints within thevehicle, and/or other considerations.

Referring now to FIG. 15, additional embodiments of the MIVT 715 will bediscussed according to example embodiments. The MIVT 715 may besubstantially similar to the embodiment of the MIVT 515 of FIG. 12 inseveral respects. Therefore, common features will not be explainedagain. Also, components in FIG. 15 that correspond to those of FIG. 12will be identified with corresponding reference numbers increased by200.

The MIVT 715 may differ from the embodiment of FIG. 12 in that theengine shaft 709 may be substantially coaxial with the central axis offirst planetary gearset 708. In other respects, the MIVT 715 may besimilar to the embodiment of FIG. 12. For example, the MIVT 715 may havethe six forward transmission modes and at least one reverse transmissionmode using the same clutching patterns discussed above with respect tothe embodiment of FIG. 12.

The embodiment of FIG. 15 may be configured for work vehicles withcertain space constraints and/or particular architectures. For example,the embodiment of FIG. 15 may be useful for “short-drop” workvehicles—those with the engine 702 relatively low and disposed rearwardtoward the cab of the work vehicle. In contrast, the embodiment of FIG.12 may be useful for “long-drop” work vehicles—those with engines 502relatively high and disposed over the front axle.

Referring now to FIG. 16, a second modular configuration of the MIVT715′ is shown. As shown, the MIVT 715′ may be substantially similar tothe MIVT 715 of FIG. 15, except the second planetary gearset 722 of FIG.15, the associated gears, and the fifth clutch 778 may be omitted in theconfiguration of FIG. 14. Thus, the embodiment of FIG. 16 does notprovide the powered-zero, co-generation capabilities of the MIVT 715 ofFIG. 15. However, as explained above with respect to FIG. 14, thiscapability may not be necessary for some vehicles. Also, the MIVT 715′of FIG. 16 may be more compact than the MIVT 715 of FIG. 15.Accordingly, the MIVT 715′ of FIG. 16 may be useful in a vehicle withparticular space constraints.

The terminology used herein is for the purpose of describing particularembodiments only and is not intended to be limiting of the disclosure.As used herein, the singular forms “a”, “an” and “the” are intended toinclude the plural forms as well, unless the context clearly indicatesotherwise. It will be further understood that any use of the terms“comprises” and/or “comprising” in this specification specifies thepresence of stated features, integers, steps, operations, elements,and/or components, but do not preclude the presence or addition of oneor more other features, integers, steps, operations, elements,components, and/or groups thereof.

The description of the present disclosure has been presented forpurposes of illustration and description, but is not intended to beexhaustive or limited to the disclosure in the form disclosed. Manymodifications and variations will be apparent to those of ordinary skillin the art without departing from the scope and spirit of thedisclosure. Explicitly referenced embodiments herein were chosen anddescribed in order to best explain the principles of the disclosure andtheir practical application, and to enable others of ordinary skill inthe art to understand the disclosure and recognize many alternatives,modifications, and variations on the described example(s). Accordingly,various other implementations are within the scope of the followingclaims.

What is claimed is:
 1. A work vehicle comprising: an engine with anengine shaft; a first infinitely variable power (IVP) machine; a secondinfinitely variable power (IVP) machine; an output shaft; and aninfinitely variable transmission (IVT) having a plurality oftransmission modes, the IVT configured to transmit power among theengine, the first IVP machine, the second IVP machine, and the outputshaft along different paths in different ones of the plurality oftransmission modes, the IVT including: a plurality of clutches, eachconfigured to engage and alternately disengage; a double planetarygearset including a first transmission component, a second transmissioncomponent and a third transmission component; and a single planetarygearset including a fourth transmission component, a fifth transmissioncomponent, and a sixth transmission component; wherein, in a firsttransmission mode of the IVT, a first subset of the plurality ofclutches is engaged, allowing transmission of engine power from theengine to the first transmission component, and allowing transmission ofIVP power between the second IVP machine and the second transmissioncomponent; wherein, in the first transmission mode, the thirdtransmission component combines the engine power and the IVP power intofirst combined power that is transmitted from the third transmissioncomponent to the fourth transmission component; and wherein, in thefirst transmission mode, the fifth transmission component transmitsreturn power to the engine shaft, and the sixth transmission componentcombines the first combined power and the return power into secondcombined power that is output to the output shaft for rotating theoutput shaft at a range of rotational speeds.
 2. The work vehicle ofclaim 1, wherein the range of rotational speeds includes a zero RPMspeed at which torque is maintained at the output shaft and a non-zeroRPM creeper speed; and wherein, in a second transmission mode of theIVT, a second subset of the plurality of clutches is engaged, allowingtransmission of engine power from the engine to one of the first,second, and third transmission components, and allowing transmission ofIVP power between the second IVP machine and another of the first,second, and third transmission components; wherein, in the secondtransmission mode, the remaining one of the first, second, and thirdtransmission components combines the engine power and the IVP power intothird combined power that is output to the output shaft; and wherein, inthe second transmission mode, the third combined power bypasses thesingle planetary gearset and is output to the output shaft.
 3. The workvehicle of claim 1, wherein the first IVP machine is a first electricmachine, and wherein the second IVP machine is a second electricmachine.
 4. The work vehicle of claim 3, wherein the first electricmachine has a generator mode and a motor mode; wherein the firstelectric machine, when in the generator mode, is configured to generateelectrical energy from mechanical energy input to the first electricmachine; wherein the second electric machine has a generator mode and amotor mode; wherein the second electric machine, when in the generatormode, is configured to generate electrical energy from mechanical energyinput to the second electric machine; and wherein, in the firsttransmission mode of the IVT, the first electric machine and the secondelectric machine are configured to simultaneously be in generator modefor cogeneration of electrical power.
 5. The work vehicle of claim 4,wherein the plurality of transmission modes of the IVT includes thefirst transmission mode and a second transmission mode; wherein, in thesecond transmission mode, the first electric machine is configured to bein either the generator mode or the motor mode; and wherein the secondelectric machine is configured to be in the motor mode.
 6. The workvehicle of claim 5, wherein the plurality of transmission modes of theIVT includes the first transmission mode, the second transmission mode,and a third transmission mode; and wherein, in the third transmissionmode, a second subset of the plurality of clutches is engaged, allowingtransmission of engine power from the engine to one of the first,second, and third transmission components, and allowing transmission ofIVP power between the second IVP machine and another of the first,second, and third transmission components; wherein, in the thirdtransmission mode, the remaining one of the first, second, and thirdtransmission components combines the engine power and the IVP power intothird combined power that is output to the output shaft; and wherein, inthe third transmission mode, the third combined power bypasses thesingle planetary gearset and is output to the output shaft.
 7. The workvehicle of claim 1, wherein the plurality of transmission modes of theIVT includes the first transmission mode, and a second transmissionmode; wherein in the first transmission mode, the first transmissioncomponent is a first set of planet gears, the second transmissioncomponent is a first sun gear, and the third transmission component is afirst ring gear that is engaged for rotation with a second set of planetgears of the double planetary gear set; wherein in the secondtransmission mode, a second subset of the plurality of clutches isengaged, allowing transmission of engine power from the engine to asecond ring gear of the double planetary gearset, and allowingtransmission of IVP power from the second electric machine to a secondsun gear of the double planetary gearset; and wherein in the secondtransmission mode, the second set of planet gears combines engine powerand IVP power into first combined power that is output to the singleplanetary gearset.
 8. The work vehicle of claim 7, wherein in the secondtransmission mode, the first combined power is output to a sun gear ofthe single planetary gearset; wherein in the second transmission mode, aring gear of the single planetary gearset outputs return power to theengine shaft; and wherein in the second transmission mode, a set ofplanet gears of the single planetary gearset combines the first combinedpower and the return power into second combined power that is output tothe output shaft.
 9. The work vehicle of claim 1, wherein the fourthtransmission component includes a sun gear of the single planetarygearset; wherein the fifth transmission component includes a ring gearof the single planetary gearset; wherein the sixth transmissioncomponent includes a plurality of planet gears of the single planetarygearset, the plurality of planet gears being connected by a carrier; andwherein, in the first transmission mode, the carrier outputs the secondcombined power to the output shaft to maintain torque at the outputshaft while the rotational speed of the output shaft is approximatelyzero.
 10. The work vehicle of claim 1, wherein the engine shaft isconfigured to rotate about an axis of rotation; wherein the doubleplanetary gearset has a central axis; and wherein the central axis andthe axis of rotation are co-axial.
 11. The work vehicle of claim 1,wherein the first IVP machine is a first electric machine; wherein thesecond IVP machine is a second electric machine; further comprising animplement that is in electrical connection with at least one of thefirst electric machine and the second electric machine; and wherein theimplement is configured to receive electrical power supplied by the atleast one of the first electric machine and the second electric machine.12. A work vehicle comprising: an engine with an engine shaft; aninfinitely variable power (IVP) source having a first electric machineand a second electric machine; an output shaft; and an infinitelyvariable transmission (IVT) having a plurality of transmission modes,the IVT configured to transmit power among the engine, the firstelectric machine, the second electric machine, and the output shaftalong different paths in different ones of the plurality of transmissionmodes, the IVT including: a plurality of clutches, each configured toengage and alternately disengage; a first planetary gearset including afirst transmission component, a second transmission component and athird transmission component; and a second planetary gearset including afourth transmission component, a fifth transmission component, and asixth transmission component; wherein, in a first transmission mode ofthe IVT, a first subset of the plurality of clutches is engaged,allowing transmission of engine power from the engine to the firsttransmission component, and allowing transmission of IVP power betweenthe second electric machine and the second transmission component;wherein, in the first transmission mode, the third transmissioncomponent combines the engine power and the IVP power into firstcombined power that is transmitted from the third transmission componentto the fourth transmission component; wherein, in the first transmissionmode, the fifth transmission component transmits return power to theengine shaft; wherein, in the first transmission mode, the sixthtransmission component combines the first combined power and the returnpower into second combined power; wherein the second combined power ofthe first transmission mode provides the output shaft with a range ofrotational speeds; wherein the first electric machine has a generatormode and a motor mode; wherein the first electric machine, when in thegenerator mode, is configured to generate electrical energy frommechanical energy input to the first electric machine; wherein thesecond electric machine has a generator mode and a motor mode; whereinthe second electric machine, when in the generator mode, is configuredto generate electrical energy from mechanical energy input to the secondelectric machine; and wherein, in the first transmission mode of theIVT, the first electric machine and the second electric machine areconfigured to simultaneously be in generator mode for cogeneration ofelectrical power.
 13. The work vehicle of claim 12, wherein the rangeincludes a powered zero speed; wherein the second combined powermaintains torque at the output shaft at the powered zero speed.
 14. Thework vehicle of claim 12, wherein the first planetary gearset is adouble planetary gearset; and wherein the second planetary gearset is asingle planetary gearset.
 15. The work vehicle of claim 14, wherein theplurality of transmission modes of the IVT includes the firsttransmission mode, and a second transmission mode; wherein in the firsttransmission mode, the first transmission component is a first set ofplanet gears, the second transmission component is a first sun gear, andthe third transmission component is a first ring gear that is engagedfor rotation with a second set of planet gears of the first planetarygear set; wherein in the second transmission mode, a second subset ofthe plurality of clutches is engaged, allowing transmission of enginepower from the engine to a second ring gear of the first planetarygearset, and allowing transmission of IVP power from the second electricmachine to a second sun gear of the first planetary gearset; and whereinin the second transmission mode, the second set of planet gears combinesengine power and IVP power into first combined power that is output tothe second planetary gearset.
 16. The work vehicle of claim 12, whereinthe plurality of transmission modes of the IVT includes the firsttransmission mode and a second transmission mode; wherein, in the secondtransmission mode, the first electric machine is configured to be ineither the generator mode or the motor mode; and wherein the secondelectric machine is configured to be in the motor mode.
 17. The workvehicle of claim 16, wherein the plurality of transmission modes of theIVT includes the first transmission mode, the second transmission mode,and a third transmission mode; and wherein, in the third transmissionmode, a second subset of the plurality of clutches is engaged, allowingtransmission of engine power from the engine to one of the first,second, and third transmission components, and allowing transmission ofIVP power between the second electric machine and another of the first,second, and third transmission components; wherein, in the thirdtransmission mode, the remaining one of the first, second, and thirdtransmission components combines the engine power and the IVP power intothird combined power that is output to the output shaft; and wherein, inthe third transmission mode, the third combined power bypasses thesecond planetary gearset and is output to the output shaft.
 18. The workvehicle of claim 12, wherein the fourth transmission component includesa sun gear of the second planetary gearset; wherein the fifthtransmission component includes a ring gear of the second planetarygearset; wherein the sixth transmission component includes a pluralityof planet gears of the second planetary gearset, the plurality of planetgears being connected by a carrier; and wherein, in the firsttransmission mode, the carrier outputs the second combined power to theoutput shaft.
 19. The work vehicle of claim 12, wherein the engine shaftis configured to rotate about an axis of rotation; wherein the firstplanetary gearset has a central axis; and wherein the central axis andthe axis of rotation are co-axial.
 20. The work vehicle of claim 12,further comprising an implement that is in electrical connection with atleast one of the first electric machine and the second electric machine.